Drive device of a working machine, drive train and working machine

Abstract

The present invention relates to a drive device (10) for a bogie-type working machine comprising a traction motor (30) designed as an electric machine and a distribution gearbox (32) with a first output shaft (38) for driving a pivotable first axle assembly (20) of the working machine and a second output shaft (40) arranged coaxially with the first output shaft (38) for driving a pivotable second axle assembly (22) of the working machine. The two axle assemblies (20, 22) each have at least one first output element (24) and one second output element (24), which are arranged parallel to each other and offset from one another. The distribution gearbox (32) is designed to provide a differential function between the first axle assembly (20) and the second axle assembly (22). The invention also relates to a drive train and a drive motor.

Description

Technical field

[0001] The present invention relates to a drive device for a working machine with a traction motor designed as an electric machine. The invention also relates to a drive train and to a working machine. State of the art

[0002] Drive systems with traction motors designed as electric machines are known for construction machinery. It is also known to use bogie axles in construction machinery. This allows the static axle load of output elements arranged one behind the other in the longitudinal direction of the vehicle to be the same and independent of suspension travel. Bogie axles can improve the off-road capability of construction machinery and protect the ground. However, bogie axles are complex and require a lot of installation space. Description of the invention

[0003] A first aspect concerns a drive device for a bogie-type machine. In a bogie design, two output elements on each side can be connected to the machine via a pivotable support. The support can, for example, be designed as a balance beam. Alternatively, the output elements can be mounted on leaf springs rotatably attached to a vehicle frame. The drive device can have a bogie axle. The bogie-type drive device can also be a special type of double axle.

[0004] The drive unit comprises a traction motor designed as an electric machine. The drive unit can be configured to provide power for driving the machine. The machine can be, for example, an agricultural or construction machine. Examples include a harvester, combine harvester, tipper loader, grader, or articulated tractor. The electric motor can be, for example, a synchronous or asynchronous motor. It can also be designed for energy recuperation. The machine can include an energy storage device and a control unit for operating the drive unit. The traction motor can have a motor shaft at which the driving force generated by the traction motor is applied.

[0005] The electric traction motor can be supplied with the electrical energy required for its operation, for example, from a battery storage system, a fuel cell, or via a diesel-powered generator. A combination of these electrical supply options is also conceivable and preferred; in particular, the electric traction motor can be supplied electrically by a battery storage system and a diesel-powered generator, or by a battery storage system and a fuel cell.

[0006] The drive device further comprises a distribution gearbox with a first output shaft for driving a first axle assembly of the driven machine and a second output shaft for driving a second axle assembly of the driven machine. The first axle assembly is pivotable. The second axle assembly is pivotable. For example, both axle assemblies are rotatably mounted on the vehicle frame. An axis of rotation of each axle assembly can extend transversely to the vehicle. The axes of rotation of the two axle assemblies can be arranged coaxially with each other. The first axle assembly can form a left side of a bogie axle and the second axle assembly a right side of a bogie axle. The two axle assemblies can be pivotable independently of each other. The two axle assemblies can be symmetrical with respect to each other. The drive device can be symmetrical.A pivot axis of the beam can, for example, extend orthogonally to the longitudinal extent of the beam at the midpoint of its longitudinal extent. The beam can extend longitudinally, for example, in the forward-reverse direction of the machine, and alternatively or additionally, the beam can extend longitudinally orthogonally to the output shafts of the transfer case.

[0007] The two output shafts are arranged coaxially. The two output shafts can, for example, share a common axis of rotation. The two output shafts can be arranged parallel to, coaxially with, or transversely to the traction motor. The axis of rotation of the two output shafts can be parallel to an axis of rotation of the traction motor. The axis of rotation of the traction motor can be defined by its motor shaft. The axes of rotation of the output shafts can be coaxial with a pivot axis of the first axle assembly and a pivot axis of the second axle assembly. The motor shaft can be mechanically coupled to the input shaft of the transfer case. This can be achieved, for example, by a spur gear stage or another power transmission element, such as a traction element. The traction element can, for example, be a chain. The power transmission element can also be a bevel gear drive.Alternatively, the motor shaft can, for example, be permanently and rotationally fixed to the input shaft of the transfer case.

[0008] Each of the two axle assemblies has at least one first output element and one second output element. The two output elements of an axle assembly can be mechanically connected to the associated output shaft of the transfer case. For example, the first and second output elements of the first axle assembly are mechanically connected to the first output shaft, and the first and second output elements of the second axle assembly are connected to the second output shaft. The two output elements of each axle assembly are arranged parallel to each other, offset from one another. For example, one of the two output elements of each axle assembly is arranged parallel to the two output shafts of the transfer case. For example, the two output elements of each axle assembly are arranged parallel to the two output shafts of the transfer case, offset from each other.For example, the two output elements of each axle assembly are arranged parallel to the axis of rotation of the respective axle assembly, about which it can pivot. For example, the first output element is arranged in front of the second output element in the direction of travel. The output elements of each axle assembly are, for example, arranged at opposite ends of the respective carrier. An output element can, for example, be a vehicle wheel, a coupling element for a vehicle wheel, or a drive pinion for driving a track.

[0009] Both axle assemblies are driven jointly by the traction motor, for example. The two output shafts are each mechanically connected to the output elements of their respective axle assemblies. The first output shaft is assigned to the first axle assemblies, and the second output shaft is assigned to the second axle assemblies. Each axle assemblies can have a connecting gear, with an input shaft of the connecting gear being mechanically connected to the corresponding output shaft of the transfer case. The connecting gear can transmit drive power, for example, applied to its input shaft, to the output elements. The input shaft of the connecting gear is, for example, permanently and rotationally fixed to the corresponding output shaft of the transfer case. The connecting gear can, for example, have one or more spur gear stages and, alternatively or additionally, planetary gear sets.

[0010] The drive unit is designed to transmit drive power from the traction motor via the transfer case to the two output shafts. Appropriate mechanical connections may be provided for this purpose. The transfer case may be designed to distribute drive power from the traction motor to the two output shafts and thus to the two axle arrangements. This distribution may be fixed or variable.

[0011] The transfer case is designed to provide a differential function between the first and second axle arrangements. This allows, for example, the drive elements on the left side to rotate at a different speed than the output elements on the right side. The transfer case can accommodate a speed differential between the two output shafts. Furthermore, the applied torque can be variably distributed between the two output shafts. This compact drive system, requiring few components, provides a particularly off-road capable drive for construction machinery. Additionally, both sides of the drive system can be driven together, for example, centrally, by a single electric motor.

[0012] Additionally, the transfer case can provide a gear ratio between its input shaft and the output shafts. The transfer case can, for example, be designed as a reduction gear. The input shaft of the transfer case can be mechanically connected to the traction motor. The transfer case can be designed for an adjustable gear ratio. For example, it can be designed to provide two different gears. However, the gear ratio of the transfer case can also be fixed and not adjustable.

[0013] The traction motor and, alternatively or additionally, the transfer case can be arranged between the first and second axle assemblies, for example, in the left-right direction of the machine. Alternatively or additionally, the traction motor and, alternatively or additionally, the transfer case can also be arranged along an axis defined by the axial extension of the two output shafts between the first and second axle assemblies. The transfer case can form a transverse differential for the drive unit. The axle assemblies can have a brake by means of which the output elements can be braked and locked.

[0014] The described arrangement of the output shafts and the traction motor allows the drive unit to be compact and mechanically simple. For example, the outer diameter of the traction motor can be smaller than or equal to the outer diameter of the transfer case. This simplifies integration. The transfer case and the traction motor can be mounted together or separately on the driven machine. They can share a common housing or have separate housings. The transfer case can, for example, have a planetary or spur gear design. It can incorporate both planetary and spur gear sets. The drive unit, and the driven machine as a whole, can be free of additional traction motors.

[0015] In one embodiment of the drive device, the traction motor is arranged coaxially with the transfer case. For example, the motor shaft can be arranged coaxially with the input shaft. Alternatively, the motor shaft of the traction motor can be arranged coaxially with the first and second output shafts. The input shaft can be arranged coaxially with both output shafts. The motor shaft can extend in the left-right direction of the machine. This allows the drive device to require very little installation space in the radial direction between the two shaft arrangements. The traction motor can also be arranged parallel to the axis offset from the transfer case. For this purpose, the motor shaft can be mechanically connected to the input shaft of the transfer case via a spur gear stage. With an axially offset arrangement, the axial installation space requirement can be minimal.The traction motor can also be arranged transversely, particularly orthogonally, to the transfer case. For this purpose, the motor shaft can be mechanically connected to the input shaft of the transfer case via a bevel gear. With a transverse orientation to the transfer case, installation space within the machine can be utilized efficiently in the longitudinal direction, and the track width of the machine can be particularly narrow. The output shafts of the transfer case, and alternatively or additionally, the output shafts, can extend in a clockwise-counterclockwise direction and thus transversely within the machine.

[0016] In one embodiment of the drive device, the traction motor has a hollow shaft. A central through-hole can be provided in the hollow shaft. The second output shaft can extend through the motor shaft. This allows an axle assembly to be connected axially to the traction motor on both sides without the need for additional spur gear stages, for example. The traction motor can thus be easily positioned centrally and transversely within the machine, for example, between the two axle assemblies. Alternatively, the motor shaft can be free of through-holes and designed as a solid shaft.

[0017] In one embodiment of the drive device, the transfer case is designed to lock the differential function. For example, the transfer case can have a switching element for this purpose. By actuating the switching element, the rotational speed of the two output shafts can be made identical, thus preventing any differential speed. When actuated, the switching element, for example, locks a planetary gear set or connects the two output shafts in a rotationally fixed manner. Locking the differential function can, for example, improve off-road capability.

[0018] In one embodiment of the drive device, the transfer case comprises a first planetary gear set with a first rotating element, a second rotating element, and a third rotating element, as well as a second planetary gear set with a first rotating element, a second rotating element, and a third rotating element. The first rotating element of a planetary gear set can, for example, be configured as a sun gear. The first and second planetary gear sets can be configured as negative planetary gear sets or positive planetary gear sets. Any further planetary gear sets of the transfer case can also be configured as negative planetary gear sets or positive planetary gear sets. If a planetary gear set is configured as a negative planetary gear set, its second rotating element can be formed by a planet carrier and its third rotating element by a ring gear.If a planetary gear set is designed as a plus planetary gear set, its second rotating element can be a ring gear and its third rotating element a planet carrier. In a planetary gear set, one or more planet gears can be rotatably mounted on the planet carrier and mesh with the external teeth of the sun gear and the internal teeth of the ring gear. In a minus planetary gear set, for example, only one set of planet gears is provided, with each planet gear meshing with the sun gear and the ring gear. In a plus planetary gear set, for example, two sets of planet gears are provided, with the planet gears of the first set meshing with the sun gear and the planet gears of the second set. The planet gears of the second set mesh accordingly with the ring gear and the planet gears of the first set.The two planetary gear sets allow for a large gear ratio in a compact design with few components, while also easily integrating the differential function. The transfer case can, for example, be free of any additional planetary gear sets beyond the two or three described here, and optionally also free of spur gear stages.

[0019] The first rotating element of the first planetary gear set can form an input shaft of the transfer case. The third rotating element of the first planetary gear set can be permanently and non-rotatably connected to the first rotating element of the second planetary gear set. The second rotating element of the second planetary gear set can be fixed to a stationary component. This stationary component could be, for example, a housing or a section of a vehicle frame. The second rotating element of the second planetary gear set can, for example, be permanently and non-rotatably connected to the stationary component. This allows for a compact and efficient transfer case. The second output shaft can, for example, extend axially towards the traction motor. The first output shaft can extend axially away from the traction motor. The first planetary gear set can be located on the side of the transfer case facing axially towards the traction motor.

[0020] In one embodiment of the drive device, the first and second planetary gear sets are radially stacked. The second planetary gear set can, for example, extend at least partially or completely within the same axial range as the first planetary gear set. This allows the transfer case to be very compact axially. The second planetary gear set can be arranged radially outside the first planetary gear set. For example, all rotating elements of the second planetary gear set can be arranged radially outside the first planetary gear set. This results in a very compact axial design, which allows the transfer case and the traction motor to be conveniently arranged coaxially side-by-side in the transverse direction of the vehicle within the machine. The transfer case can still have a diameter that is less than or equal to the diameter of the traction motor.The first ring gear and the second sun gear can, for example, be formed as a single piece. Internal teeth can form the first ring gear section, and external teeth the second sun gear section. The first ring gear and the second sun gear can also be formed by a sun gear ring and, for example, be formed as a single piece. Alternatively, the first and second planet gear sets can be arranged axially side by side and occupy at least part of the same radial area. This allows the radial space requirement of the transfer case to be very small. Additional planet gear sets can, for example, be arranged axially next to the first and second planet gear sets or stacked radially with one or both of them.

[0021] In one embodiment of the drive device, the second rotating element of the first planetary gear set forms the second output shaft. The third rotating element of the second planetary gear set can form the first output shaft. This allows for a high gear ratio and uniform torque distribution to be easily achieved.

[0022] In one embodiment of the drive device, the first rotating element of the first planetary gear set is configured as the first sun gear. The second rotating element of the first planetary gear set can be configured as the first planet carrier. The third rotating element of the first planetary gear set can be configured as the first ring gear. The first rotating element of the second planetary gear set can be configured as the second sun gear. The second rotating element of the second planetary gear set can be configured as the second planet carrier. The third rotating element of the second planetary gear set can be configured as the second ring gear. The first and second planetary gear sets can be configured as negative planetary gear sets.

[0023] The numbering of the rotating elements can be used to assign them to a planetary gear set. For example, designating it as the second sun gear can uniquely identify it as belonging to the second planetary gear set. Accordingly, the second planetary gear set might only have a single sun gear.

[0024] The first sun gear can thus form an input shaft of the transfer case. The first planet carrier can form the second output shaft. The first ring gear can be permanently and rotationally fixed to the second sun gear. The second planet carrier can be fixed to the stationary component. The second ring gear can form the first output shaft. The first sun gear can be mechanically connected to the motor shaft. If a locking mechanism for the differential function is provided, the second ring gear and the first planet carrier can, for example, be rotationally fixed by means of the locking device.

[0025] A rotationally fixed connection between two elements is understood to be a connection in which the two elements are essentially rigidly coupled to each other in all intended states. This also includes a friction-fit connection, in which slippage may occur. Permanently rotationally fixed elements can, for example, exist as permanently rotationally fixed individual components or as a single piece.

[0026] A connection between two elements via another element can mean that this additional element is involved in an indirect functional connection between the two elements. For example, this element can be positioned in the force flow between these two elements. A connection between two elements via two or more elements can mean that these additional elements are all involved in an indirect functional connection between the two elements. A switchable connection can, in one state, enable torque transmission between two elements, for example, through a rigid coupling, and, in another state, essentially interrupt this torque transmission. A corresponding switching element can be provided between the two elements for this purpose. If two elements can be connected in a rotationally fixed manner, these two elements can, for example, be connected to each other in a rotationally fixed manner via a switching element.If two elements can be mechanically connected, these two elements can, for example, be connected via a switching element for torque transmission.

[0027] A planetary gear set is configured, for example, as a negative planetary gear set or a positive planetary gear set. The sun gears, planet carriers, and ring gears of a planetary gear set constitute its rotating elements. Each planetary gear set can have one or more planet gears, which are rotatably mounted on the planet carrier. For example, the planet gears of a planetary gear set mesh with a sun gear and a ring gear of the same planetary gear set. Each planetary gear set can be free of elements other than those mentioned here. A rotational axis of a planetary gear set can correspond to a rotational axis of its rotating elements.

[0028] In one embodiment of the drive device, the transfer case is provided with a third planetary gear set comprising a first rotating element, a second rotating element, and a third rotating element. The third rotating element of the second planetary gear set can then form the first output shaft. The first rotating element of the third planetary gear set can be permanently and rotationally fixed to the third rotating element of the second planetary gear set. The second rotating element of the third planetary gear set can form the second output shaft. The third rotating element of the third planetary gear set can be permanently and rotationally fixed to the second rotating element of the first planetary gear set. The third planetary gear set can be arranged downstream of the first and second planetary gear sets in the torque flow to the output shafts. The transfer case can be free of any further planetary gear sets.The third planetary gear set allows for a particularly high gear ratio through the transfer case. If the transfer case is designed to lock the differential, the third planetary gear set can, for example, be locked in place. When a planetary gear set is locked, two of its rotating elements are connected in a rotationally fixed manner, so that all rotating elements rotate at the same angular velocity and rotational speed. This allows the two output shafts to be coupled together in a rotationally fixed way.

[0029] In one embodiment of the drive device, it is provided that the first rotating element of the first planetary gear set is designed as the first sun gear.

[0030] The second rotating element of the first planetary gear set can be configured as the first planet carrier. The third rotating element of the first planetary gear set can be configured as the first ring gear. The first rotating element of the second planetary gear set can be configured as the second sun gear. The second rotating element of the second planetary gear set can be configured as the second planet carrier. The third rotating element of the second planetary gear set can be configured as the second ring gear. The first rotating element of the third planetary gear set can be configured as the third sun gear. The second rotating element of the third planetary gear set can be configured as the third planet carrier. The third rotating element of the third planetary gear set can be configured as the third ring gear. The three planetary gear sets can be configured as negative planetary gear sets. The numbering can again serve to assign them to their respective planetary gear sets.

[0031] In one embodiment of the drive device, the two output shafts are mechanically connected to the two output elements via a final drive. The final drive can, for example, comprise a spur gear stage or a planetary gear set. The final drive can distribute power from the connected output shaft of the transfer case to the output elements of the associated axle assembly. This distribution can be fixed; for example, half of the transmitted torque can be transferred to each of the two output elements. The final drive can form part of the previously described connecting gear. The connecting gear can also consist entirely of the final drive.For example, the first output shaft can be mechanically connected to the first and second output elements of the first axle assembly via a first final drive. Alternatively, the first output shaft can be mechanically connected to the first output element of the first axle assembly via a first final drive and to the second output element of the first axle assembly via a second final drive. For example, the second output shaft can be mechanically connected to the first and second output elements of the second axle assembly via a second final drive. Alternatively, the second output shaft can be mechanically connected to the first output element of the second axle assembly via a first final drive and to the second output element of the second axle assembly via a second final drive. The final drives can be mounted on the support.For example, individual elements of the final translation can be included in the carrier.

[0032] In one embodiment of the drive device, it is designed as a portal bogie axle. With a portal bogie axle, for example, the axis of rotation of the output elements can be offset vertically from the support. This can increase ground clearance. For example, a gear stage can be provided in the output element for this purpose. This gear stage can, for example, be a spur gear stage. A spur gear stage can, for example, consist of one or more meshing gears.

[0033] In one embodiment of the drive device, the drive device includes a transmission that is switchable between a first gear ratio and at least one second gear ratio for transmitting drive power from the traction motor to the transfer case. The transmission can, for example, provide two or more gears. The transmission can also be configured to disengage the traction motor from the transfer case. For this purpose, the transmission can be designed to provide a neutral position. The transmission can be located in the torque path between the traction motor and the transfer case. The transmission allows for a wider range of driving speeds. The transmission can include shift elements, spur gear stages, and, alternatively or additionally, planetary gear sets.For example, the transmission can be configured to connect the engine shaft to the input shaft of the transfer case via a first spur gear stage and a second spur gear stage, the first spur gear stage having a different gear ratio than the second spur gear stage. A shifting element provided for this purpose in the transmission can, for example, be designed as a double synchronizer. The transmission can have an input shaft that is arranged coaxially with the engine shaft. The transmission can have an output shaft that is arranged coaxially with the input shaft of the transfer case. The transmission can have only axes of rotation that are arranged coaxially with the input shaft of the transfer case. If no transmission is provided, the engine shaft can, for example, be permanently and rotationally fixed to the input shaft of the transfer case.

[0034] A second aspect concerns the drivetrain. The drivetrain includes a drive device as described in the first aspect. The respective advantages and further features are detailed in the description of the first aspect, whereby embodiments of the first aspect also form embodiments of the second aspect and vice versa. The drivetrain also includes a first axle arrangement and a second axle arrangement, which may be connected or connectable to the associated output shafts of the transfer case, for example. The drivetrain may additionally include further motors, such as additional electric motors. Furthermore, the drivetrain may include pumps driven by these motors. This allows, for example, consumers such as power steering, working hydraulics, or switching elements to be supplied with hydraulic pressure. The pumps may be designed as fixed-displacement or variable-displacement pumps.The drivetrain may also include a power take-off unit. The drivetrain may be designed to provide driving power and, optionally, work power.

[0035] A third aspect concerns a machine with a drive train according to the second aspect and, alternatively or additionally, a drive device according to the first aspect. The respective advantages and further characteristics can be found in the descriptions of the first and second aspects, whereby embodiments of the third aspect also constitute embodiments of the first and second aspects, respectively, and vice versa. The machine may have a chassis to which the drive train or drive device is attached. The axle assemblies may be pivotably mounted on the chassis. The machine can be driven by the drive train, for example, for driving. The drive force of the machine may be provided electrically via the drive train. Brief description of the characters Fig. Figure 1 illustrates in a schematic side view a working machine with a drive device in bogie construction. Fig. Figure 2 schematically illustrates a first embodiment of a bogie axis in a perspective view. Fig. Figure 3 schematically illustrates a second embodiment of a bogie axis in a perspective view. Fig. Figure 4 schematically illustrates a first embodiment of a drive device for the working machine. Fig. Figure 5 schematically illustrates a second embodiment of a drive device for the working machine. Fig. Figure 6 schematically illustrates a third embodiment of a drive device for the working machine. Fig. Figure 7 schematically illustrates a fourth embodiment of a drive device for the working machine. Fig. Figure 8 schematically illustrates a fifth embodiment of a drive device for the working machine. Fig. Figure 9 schematically illustrates a sixth embodiment of a drive device for the working machine. Fig. Figure 10 schematically illustrates a seventh embodiment of a drive device for the working machine. Fig. Figure 11 schematically illustrates an eighth embodiment of a drive device of the working machine. Fig. Figure 12 schematically illustrates a locking of a differential function in embodiments of the drive train in which a transfer case has two planetary gear sets. Fig. Figure 13 schematically illustrates a locking of a differential function in embodiments of the drive train in which a transfer case has three planetary gear sets. Detailed description of embodiments

[0036] Fig. Figure 1 illustrates a schematic side view of a harvester. The machine has a bogie-type drive unit 10. A steerable, non-driven front axle 12 has a wheel 14 on each side. A rear axle 16 has a first pivotable axle assembly 20 on the left side of the vehicle. On the right side, the rear axle 16 has a second pivotable axle assembly 22. Each axle assembly 20, 22 has a first and a second driven output element 24, here in the form of wheels 14, which are arranged parallel to each other and offset from one another. The output elements 24 are rotatably mounted on opposite ends of an associated support 26 in the longitudinal direction of the vehicle.The drive elements 24 of the first axle arrangement 20 roll on a substantially level surface, which is why the support 26 extends substantially parallel to the surface and thus horizontally. A front drive element 24 of the two drive elements of the second axle arrangement 22 rolls over an obstacle, which is why the support 26 pivots. This results in a uniform, gentle load on the surface and high off-road capability.

[0037] In Fig. Figure 2 shows a first variant of the drive device 10 with the two axle arrangements 20, 22 in a schematic perspective view. The output elements 24 are designed here only as the coupling element to which the vehicle wheels 14 with their rims are permanently and rotationally fixed. In the transverse direction of the vehicle, the two supports 26 are connected to each other via a housing 28, which forms a stationary component. The supports 26 are pivotably mounted on the housing 28. A traction motor 30, designed as an electric machine, and a distribution gearbox 32 are housed in the housing 28; their details will be described with reference to the following figures. This results in a compact drive integrated into the bogie axle.

[0038] In Fig. Figure 3 shows a second variant of the drive device 10 with the two axis arrangements 20, 22 in a schematic perspective view. This differs from the Fig. 2. This is achieved by the fact that the drive device 10 is designed here in a portal-bogie construction. For this purpose, a pivot axis of the output elements 24 is arranged offset from a bearing area on the respective support 26. For this purpose, the output elements 24 have an integrated spur gear stage.

[0039] Fig. Figure 4 schematically illustrates a first embodiment of the drive device 10 in detail, clearly showing the arrangement of the respective axes and the mechanical connections between the components. The traction motor 30 is designed as an electric machine and has a motor shaft 34. This motor shaft 34 is connected via a distribution gearbox 32 to the axle assemblies 20 and 22 for power transmission to output elements 24. The distribution gearbox 32 has an input shaft 36, which is mechanically connected or operatively connectable to the motor shaft 34. The distribution gearbox 32 has a first output shaft 38, which is mechanically connected or operatively connected to the first axle assembly 20. The distribution gearbox 32 has a second output shaft 40, which is mechanically connected or operatively connected to the second axle assembly 22.The drive device 10 is thus designed to transmit drive power from the traction motor 30 via the distribution gearbox 32 and the two output shafts 38, 40 to the two axle assemblies 20, 22. The axle assemblies 20, 22 have a pivot axis with their support 26, which is coaxial with the two output shafts 38, 40. The support 26 is in . Fig. 4 and the following figures are not shown.

[0040] The two output shafts 38, 40 are arranged coaxially with each other and with the traction motor 30 and its motor shaft 34. The motor shaft 34 is designed as a hollow shaft, with the second output shaft 40 extending through the motor shaft 34. The transfer case 32 is designed to provide a differential function between the first axle assembly 20 and the second axle assembly 22. The two output shafts 38, 40 can rotate at different speeds.

[0041] Each axle arrangement 20, 22 has a final drive ratio 42, which in the embodiment of Fig. Figure 4 comprises a multi-stage spur gear transmission. The output shaft 38, 40 is permanently and rotationally fixedly connected to an input spur gear of the associated final drive 42. Two further spur gears mesh with this input spur gear to transmit drive power via two paths to each of the two output elements 24. The further spur gears of the final drive 42 are arranged symmetrically to the input spur gear within the carrier 26. In the first embodiment, the final drive 42 has, in addition to the input spur gear, two sets of two further spur gears operatively connected to it. In other embodiments, more or fewer spur gears are provided. An output planetary gear set 44 is integrated into each of the output elements 24. A sun gear 46 of the output planetary gear set 44 forms an input shaft. A planet carrier 48 of the output planetary gear set 44 forms an output shaft, which drives the rim.A ring gear 49 of the output planetary gear set 44 is fixed to the housing 28. The output planetary gear set 44 is designed as a negative planetary gear set. In other embodiments, a positive planetary gear set is also used. Planet gears are rotatably mounted on the planet carrier 48, which mesh with the sun gear 46 and the ring gear 49.

[0042] At the first in Fig. In the embodiment shown in Figure 4, the transfer case 32 has a first planetary gear set 50 with a first sun gear 52, a first planet carrier 54, and a first ring gear 56, as well as a second planetary gear set 60 with a second sun gear 62, a second planet carrier 64, and a second ring gear 66 as rotating elements. Both planetary gear sets 50 and 60 are designed as negative planetary gear sets. In other embodiments, positive planetary gear sets are also used. First planet gears 58 are rotatably mounted on the first planet carrier 54 and mesh with the first sun gear 52 and the first ring gear 56. Second planet gears 68 are rotatably mounted on the second planet carrier 64 and mesh with the second sun gear 62 and the second ring gear 66.The first ring gear 56 is permanently and rotationally fixed to the second sun gear 62, which are formed integrally by a sun gear featuring internal and external teeth. The two planet gear sets 50 and 60 are radially stacked, with the second planet gear set 60 located radially outside the first planet gear set 50. The second planet carrier 64 is fixed to a stationary component, in this case the housing 28. The first planet carrier 54 forms the second output shaft 40. The second ring gear 66 forms the first output shaft 38. The first sun gear 52 forms the input shaft 36. The input shaft 36 is arranged coaxially with the motor shaft 34. The axes of rotation of the output elements 24 are arranged parallel to the output shafts 38 and 40.

[0043] In the first embodiment, the transfer case 32 is designed to lock the differential function as needed. For this purpose, a switching element 18 is provided, by means of which the first output shaft 38 and the second output shaft 40 can be connected in a rotationally fixed manner. In this embodiment, the switching element 18 is connected to the first planet carrier 54 and the second ring gear 66. The switching element 18 is designed as a dog clutch in one variant and as a multi-plate clutch in another. In the first embodiment, the axle assemblies 20, 22 are permanently operatively connected to the transfer case 32 and thus to the traction motor 30. The two planetary gear sets 50, 60 are arranged coaxially to each other, with the second planetary gear set 60 being arranged radially outside the first planetary gear set 50.

[0044] The second in Fig. The embodiment shown in Figure 5 is a modification of the first embodiment. Only the differences from this embodiment are explained. In the second embodiment, the two planetary gear sets 50, 60 are arranged axially side by side. The first ring gear 56 and the second sun gear 62 are formed by two separate components arranged axially side by side. The first planetary gear set 50 is arranged axially on a side of the second planetary gear set 60 facing the traction motor 30, and thus between the traction motor 30 and the second planetary gear set 60. This results in a radially compact design.

[0045] The third in Fig. The embodiment shown in Figure 6 is a modification of the second embodiment. Only the differences from this embodiment are explained. In the third embodiment, the transfer case 32 additionally has a third planetary gear set 70, which is arranged coaxially to the two other planetary gear sets 50, 60 of the transfer case 32. The third planetary gear set 70 has a third sun gear 72, a third planet carrier 74, and a third ring gear 76. A set of third planet gears 78 meshes with the third sun gear 72 and the third ring gear 76. The third planetary gear set 70 is designed here as a negative planetary gear set. In other embodiments, the third planetary gear set 70 is designed as a positive planetary gear set. The first planetary gear set 50 is arranged axially between the second planetary gear set 60 and the third planetary gear set 70.The second planetary gear set 60 is arranged on a side of the first planetary gear set 50 facing the traction motor 30, and the third planetary gear set 70 is arranged on a side facing away from the traction motor 30.

[0046] Due to the third planetary gear set 70, the transfer case 32 is connected differently in the third embodiment. The first sun gear 52 continues to form the input shaft 36. The first output shaft 38 is permanently and rotationally fixed to the third sun gear 72. The second ring gear 66 is permanently and rotationally fixed to the third sun gear 72 and thus also to the first output shaft 38. The first planet carrier 54 is no longer permanently and rotationally fixed to the second output shaft 40, but rather permanently and rotationally fixed to the third ring gear 76. The third planet carrier 74 is permanently and rotationally fixed to the second output shaft 40 and thus forms the second output shaft 40.

[0047] The transfer case 32 can provide a particularly high gear ratio by means of the third planetary gear set 70. Therefore, the output planetary gear sets 44 were omitted in the third embodiment.

[0048] In the third embodiment, the transfer case 32 is also designed to lock the differential function. For this purpose, the switching element 18 is designed to lock the third planetary gear set 70 by connecting two rotating elements of the third planetary gear set 70 to each other in a rotationally fixed manner. In the embodiment shown, the third ring gear 76 can be rotationally fixed to the third sun gear 72 by the switching element 18.

[0049] The fourth in Fig. The embodiment shown in Figure 7 is a modification of the first embodiment. Only the differences from this embodiment are explained. In the fourth embodiment, the output planetary gear sets 44 were also omitted. Instead, the output elements 24 have an additional spur gear stage 80, with which one axis of rotation of the output elements 24 is offset to an end region of the carrier 26. In addition, the drive device 10 is designed in a portal bogie construction, as shown in Fig. 3 shown.

[0050] The fifth in Fig. The embodiment shown in Figure 8 is a modification of the first embodiment. Only the differences from this embodiment are explained. In the fifth embodiment, the traction motor 30 with its motor shaft 34 is not arranged coaxially with the input shaft 36 of the transfer case 32. The motor shaft 34 is therefore not permanently and rotationally fixed to the input shaft 36 of the transfer case 32. Instead, the traction motor 30 is arranged orthogonally to the input shaft 36 and thus also to the output shafts 38, 40 of the transfer case 32. The motor shaft 34 is mechanically connected to the input shaft 36 of the transfer case 32 via a bevel gear 90.

[0051] The sixth in Fig. The embodiment shown in Figure 9 is a modification of the first and also the fifth embodiments. Only the differences from these embodiments are explained. In the sixth embodiment, the traction motor 30, with its motor shaft 34, is arranged axially offset from the input shaft 36 of the transfer case 32. The motor shaft 34 is therefore neither permanently fixed against rotation nor connected to the input shaft 36 of the transfer case 32 via a bevel gear 90. Instead, the traction motor 30 is arranged axially offset from the input shaft 36 and thus also from the output shafts 38, 40 of the transfer case 32. The motor shaft 34 is mechanically connected to the input shaft 36 of the transfer case 32 via a spur gear stage 92.

[0052] The seventh in Fig. The embodiment shown in Figure 10 is a modification of the first embodiment. Only the differences from this embodiment are explained. In the seventh embodiment, the drive device 10 additionally has a transmission 100. The transmission 100 is switchable for transmitting the drive power from the traction motor 30 to the transfer case 32, with a first gear ratio and at least one second gear ratio. The motor shaft 34 is therefore not permanently and rotationally fixed to the input shaft 36 of the transfer case 32, but is mechanically connected via the transmission 100.

[0053] The transmission 100 has a planetary gear set 110. The planetary gear set 110 comprises a sun gear 112, a planet carrier 114, and a ring gear 116. A set of planet gears 118 is rotatably mounted on the planet carrier 114, meshing with the sun gear 112 and the ring gear 116. The planetary gear set 110 is designed as a negative planetary gear set. In other embodiments, a positive planetary gear set is also used. The transmission 100 also has a gear selector 120, which is designed as a friction-fit element in one variant and as a positive-fit element in another. In a first switching position of the gear selector 120, a rotating element of the planetary gear set 110 is locked against the stationary component, i.e., the housing 28. In the example shown, this is the ring gear 116.This provides a gear ratio between the motor shaft 34 and the transfer case 32 of a non-one ratio, here greater than one. In a second switching position of the gearshift element 120, the transmission planetary gear set 110 is locked in place by a rotationally fixed connection of two rotating elements of the transmission planetary gear set 110. In the illustrated embodiment, the gearshift element 120, in its second switching position, connects the sun gear 112 to the ring gear 116. As a result, the transmission planetary gear set 110 rotates as a unit, and no gear ratio is provided between the motor shaft 34 and the transfer case 32, or rather, the gear ratio is then one. In the illustrated example, the ring gear 116 of the transmission 100 forms its input shaft, which is permanently and rotationally fixed to the motor shaft 34.In the example shown, the planet carrier 114 of the gearbox 100 forms its output shaft, which is permanently and rotationally fixed to the input shaft 36 of the transfer gearbox 32.

[0054] The eighth in Fig. The embodiment shown in Figure 11 is a modification of the seventh and sixth embodiments. Only the differences from these embodiments are explained. As in the sixth embodiment, the traction motor 30 is arranged parallel to the input shaft 36 of the transfer case 32. As in the seventh embodiment, the traction motor 30 can be connected to the transfer case 32 via a transmission 100, which provides a first gear ratio and at least one second gear ratio. However, the transmission 100 in the eighth embodiment is designed differently than in the seventh embodiment.

[0055] Instead of a planetary gear set 110, the transmission 100 in the eighth embodiment has a first spur gear set 102 and a second spur gear set 104, which have different gear ratios. The gearshift element 120 allows the motor shaft 34 to be mechanically connected to the input shaft 36 of the transfer case 32 either via the first spur gear set 102 or the second spur gear set 104. In the illustrated embodiment, the gearshift element 120 is designed as a positive-locking double shifting element, which can be actuated with only one actuator. In another variant, two friction-locking shifting elements are provided instead.

[0056] Fig. Figure 12 illustrates a general structure of the drive device 10 with the distribution gearbox 32, comprising two planetary gear sets 50 and 60 and a lockable differential function. A rotating element of the first planetary gear set 50 is mechanically connected to the motor shaft 34. Another rotating element of the first planetary gear set 50 is connected to a rotating element of the second planetary gear set 60. Yet another rotating element of the first planetary gear set 50 is mechanically connected to the second output shaft 40 and thus to the second axle assembly 22. Another rotating element of the second planetary gear set 60 is fixed to the stationary component. Yet another rotating element of the second planetary gear set 60 is mechanically connected to the first output shaft 38 and thus to the first axle assembly 20. The switching element 18 is designed to connect the two output shafts 38 and 40 to each other in a switchable, rotationally fixed manner.

[0057] Fig.Figure 13 illustrates a general structure of the drive device 10 with the distribution gearbox 32 having three planetary gear sets. A rotating element of the first planetary gear set 50 is mechanically connected to the motor shaft 34. Another rotating element of the first planetary gear set 50 is connected to a rotating element of the second planetary gear set 60. Yet another rotating element of the first planetary gear set 50 is connected to a rotating element of the third planetary gear set 70. Another rotating element of the second planetary gear set 60 is fixed to the stationary component. Yet another rotating element of the second planetary gear set 60 is connected to another rotating element of the third planetary gear set 70. This further rotating element of the third planetary gear set 70 is mechanically connected to the first output shaft 38 and thus to the first axle assembly 20.Another rotating element of the third planetary gear set is mechanically connected to the second output shaft 40 and thus to the second axle arrangement 22.

[0058] In this embodiment, the switching element 18 is configured with three planetary gear sets to lock the third planetary gear set 70 in order to disable the differential function. Three illustrated variants exist, in each of which the switching element 18 is configured to connect a different pair of two of the three rotating elements of the third planetary gear set in a rotationally fixed manner when actuated. Typically, only a single switching element 18 is provided. Reference sign 10 Drive device 12 Front axle 14 vehicle wheel 16 Rear axle 18 switching element 20 first axle arrangement 22 second axle arrangement 24 output elements 26 carriers 28 cases 30 traction motor 32 Transfer case 34 Motor shaft 36 Input shaft 38 first output wave 40 second output wave 42 Final translation 44 Output planetary gear set 46 Sun gear of the output planetary gear set 48 planetary carriers of the output planetary gear set 49 Ring gear of the output planetary gear set 50 first planetary gear set 52 first sun wheel 54 first planetary carrier 56 first ring gear 58 first planetary gears 60 second planetary gear set 62 second sun wheel 64 second planetary carrier 66 second ring gear 68 second planetary gears 70 third planetary gear set 72 third sun wheel 74 third planetary carrier 76 third ring gear 78 third planetary gears 80, 92 Spur gear stage 90 bevel gear 100 manual transmissions 102 first spur gear set 104 second spur gear set 110 Gearbox planetary gear set 112 Sun gear of the gearbox planetary gear set 114 Planetary carrier of the gearbox planetary gear set 116 Ring gear of the gearbox planetary gear set 118 planetary gears of the gearbox planetary gear set 120 gear shift element

Claims

[1] Drive device (10) for a bogie-type working machine with a traction motor (30) designed as an electric machine and a distribution gearbox (32) with a first output shaft (38) for driving a pivotable first axle assembly (20) of the working machine and a second output shaft (40) arranged coaxially to the first output shaft (38) for driving a pivotable second axle assembly (22) of the working machine, wherein the two axle assemblies (20, 22) each have at least one first output element (24) and one second output element (24) which are arranged parallel to each other, wherein the drive device (10) is designed to transmit drive power from the traction motor (30) via the distribution gearbox (32) to the two output shafts (38, 40), wherein the distribution gearbox (32) is designed toto provide a differential function between the first axis arrangement (20) and the second axis arrangement (22). [2] Drive device (10) according to claim 1, characterized by , that the traction motor (30) is arranged coaxially with the transfer case (32). [3] Drive device (10) according to claim 1 or 2, characterized by , that the traction motor (30) has a motor shaft (34) designed as a hollow shaft, wherein the second output shaft (40) extends through the motor shaft (34). [4] Drive device (10) according to any of the preceding claims, characterized by , that the transfer case (32) is designed to lock the differential function. [5] Drive device (10) according to any of the preceding claims, characterized by, that the transfer case (32) has a first planetary gear set (50) with a first rotating element (52), a second rotating element (54) and a third rotating element (56) and a second planetary gear set (60) with a first rotating element (62), a second rotating element (64) and a third rotating element (66), wherein the first rotating element (52) of the first planetary gear set (50) forms an input shaft (36) of the transfer case (32), wherein the third rotating element (56) of the first planetary gear set (50) is permanently and rotationally fixedly connected to the first rotating element (62) of the second planetary gear set (60), wherein the second rotating element (64) of the second planetary gear set (60) is fixed to a stationary component,wherein the first planetary gear set (50) and the second planetary gear set (60) are stacked radially and wherein the second rotating element (54) of the first planetary gear set (50) forms the second output shaft (40) and that the third rotating element (66) of the second planetary gear set (60) forms the first output shaft (38). [6] Drive device (10) according to claim 5, characterized by, that the first rotating element (52) of the first planet gear set (50) is designed as the first sun gear (52), the second rotating element (54) of the first planet gear set (50) is designed as the first planet carrier (54), the third rotating element (56) of the first planet gear set (50) is designed as the first ring gear (56), the first rotating element (62) of the second planet gear set (60) is designed as the second sun gear (62), the second rotating element (64) of the second planet gear set (60) is designed as the second planet carrier (64), and the third rotating element (66) of the second planet gear set (60) is designed as the second ring gear (66). [7] Drive device (10) according to at least one of claims 1 to 4, characterized by, that the transfer case (32) has a first planetary gear set (50) with a first rotating element (52), a second rotating element (54) and a third rotating element (56) and a second planetary gear set (60) with a first rotating element (62), a second rotating element (64) and a third rotating element (66), wherein the first rotating element (52) of the first planetary gear set (50) forms an input shaft (36) of the transfer case (32), wherein the third rotating element (56) of the first planetary gear set (50) is permanently and rotationally fixed to the first rotating element (62) of the second planetary gear set (60), wherein the second rotating element (64) of the second planetary gear set (60) is fixed to a stationary component, wherein the first planetary gear set (50) and the second planetary gear set (60) are radially stacked and wherein the transfer case (32) has a third planetary gear set (70) with a first rotating element (72),a second rotating element (74) and a third rotating element (76), wherein the third rotating element (66) of the second planetary gear set (60) forms the first output shaft (38), wherein the first rotating element (72) of the third planetary gear set (70) is permanently and non-rotatably connected to the third rotating element (66) of the second planetary gear set (60), wherein the second rotating element (74) of the third planetary gear set (70) forms the second output shaft (40), and wherein the third rotating element (76) of the third planetary gear set (70) is permanently and non-rotatably connected to the second rotating element (54) of the first planetary gear set (50). [8] Drive device (10) according to claim 7, characterized by, that the first rotating element (52) of the first planetary gear set (50) is designed as the first sun gear (52), the second rotating element (54) of the first planetary gear set (50) is designed as the first planet carrier (54), the third rotating element (56) of the first planetary gear set (50) is designed as the first ring gear (56), the first rotating element (62) of the second planetary gear set (60) is designed as the second sun gear (62), the second rotating element (64) of the second planetary gear set (60) is designed as the second planet carrier (64), the third rotating element (66) of the second planetary gear set (60) is designed as the second ring gear (66), the first rotating element of the third planetary gear set (70) is designed as the third sun gear (72), the second rotating element of the third planetary gear set (70) is designed as the third planet carrier (74), and the third rotating element of the third planetary gear set (70) is designed as the third ring gear (76). [9] Drive device (10) according to any of the preceding claims, characterized by , that the two output shafts (38, 40) are each mechanically connected to the two output elements (24) via one or more final transmissions (42). [10] Drive device (10) according to one of the preceding claims, characterized by , that the drive device (10) is designed in portal-bogie construction. [11] Drive device (10) according to any of the preceding claims, characterized by , that the drive device (10) has a transmission (100) which is designed to be switchable with a first gear ratio and at least a second gear ratio for the transmission of the drive power from the traction motor (30) to the transfer gearbox (32). [12] Drive train with a drive device (10) according to one of the preceding claims, comprising a first axle arrangement (20) and a second axle arrangement (22). [13] Working machine with a drive train according to claim 12, wherein the working machine can be driven by the drive train.

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